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Nov. 6 1923.

. 1,473,157 E. g. MORGAN LOADING MACHINE Original Filed April 30, 1913 10 Sheets-Sheet 1 MVnJa/LW Nov. 6 1923, 1,473,157

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E. c. MORGAN LOADING MACHINE 1915 10 Sheets-Sheet 4 Original Filed April 50,

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E. c. MORGAN LOADING MACHINE Original Filed A ril 30, 1915 10 Sheets-$heet 6 .274 Edmund G'Mb ryan/ Gnome WWW 10 Sheets-Sheet 8 Q4 Ri anue v vfpz' Edmundfillaf'yan Q I ..m L N no & w -8. M." m o o o o g m WJH H A ME m l no 00 a w E. C. MORGAN LOAIjING MACHINE Original Filed April 30 Nov. 6 1923.

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LOADING MACHI NE Original Filed April 30, 1 3 10 Sheets-Sheet 9 LOADING MACHINE Original Filed Apri1 50, 1913 10 Sheets-Sheet 10 yaw-11x19 awvenfoz Patented Nov. 6, 1923.

UNITED ST rs rarer- EDMUND C; ll/IORGAII, OE NEW YORK, N. Y.; OLIVE EUGENIE MORGAN EXECUTRIX OF SAID EDMUND C. MORGAN, DECEASED.

LOADING MACHINE Original application filed April 30, 1913, Serial no. 764,487. Divided and this application filed May 13,

To all whom it may concern Be it known that I, EDMUND G. MORGAN, citizen or": the United States, residing in New York city, county or" New York, and State of New York, have invented a new and useful Improvement in Loading Machines, of which the following is a specification.

l ly invention relates to loading machines particularly adapted for loading coal, either in combination with mining mechanism in a. mining and loading machine, or sepa rately from said mining mechanism. The present application discloses subject-matter in common with the disclosure in my co pending application Serial No. 76%,187, filed April 30, 1913, for an improvement in mining machines. 7

One of the objects of the present invention is the provision of simplified and improved loading apparatus particularly adapted for loading coal in low roof mine chambers.

More pa"ticularly it is the object of the present invention to provide an arcuately movable conveyor at the forward end of the stationary conveyor arranged so that the forward conveyor will be continually in delivery communication with the stationary conveyer throughout a range of arcuate movement of the forward conveyor of 180 degrees or more, and to provide operating and adjusting mechanism for the loading machine.

Other objects of the invention will appear hereinafter, the novel features and combinations of elements being set forth in the appended claims.

ln my copending. application, Serial No. 764.5%87, filed April 30, 1913, for an improvement in mining machines, I have described and claimed themining mechanism shown in the present application, and also such mining mechanism combined, with the loading mechanism in C011'1l3lI1GCl mining and loading machine, as shown in the present application, whereas the'claims hereto appended in the present application are directed to theloading appa 'atus used without the mining mechanism, that is, with all of the cutting. mechanism removed or omitted. 7

Referring to the accompanying drawings,

Serial No. 286,867.

Fig. 1 is an elevational view of a mining and loading machine mounted on a truck for transportation; Fig. 2 is an elevational view of the mining and loading machine in a mine preparatory to cutting operation; Fig. 3 is a sectional elevational view on the line 33 of Fig. 5, looking in the direction of the arrows; F t is a fragmentary ver-' tical sectional view of a modification for lifting the forward portion of the mining and loading machine; Fig. 5 is a plan view of the entire mining and loading machine; Fig. 6 is a vertical sectional view taken on the line 6-6 of Fig. 5, looking in the direction of the arrows; Fig. 7 is a sectional plan view taken on the line '77 of Fig. 3; Fig.

8 is a. sectional plan view taken on the line 8-8 of Fig. 3; Fig. 9 is a side elevational view taken on the line 99 of Fig. 8, looking in the direction of the arrows; Fig. 10 is a fragmentary vertical sectional view of a modification illustrating means for auto matically controlling the speed of the cutting mechanism for cutting and noncutting operations; Fig. 11 is a plan view of a large gear by which the entire mechanism is given a rotary motion; Fig. 12 is a sectional-view of Fig. 11; Fig. 18 is a diagrammatic view showing the manner in which the entire loading machine may be shifted to various angles to change its path of travel in the mine; Fig. 1 1 is a sectional plan view of two rooms of the mine with an intervening wall and apparatus for removing dust from the mining and loading machine room to the next'adjacent room; Fig. 15 illustrates a sectional elevational view through the mine wall after the horizontal and vertical kerfs have been out by the. mining ma chine; Fig. 16 is a plan view and Fig. 17 is a longitudinal sectional elevation of an adaptation oi the loading apparatus of the other views, to very low roof mine chamhers; Fig. 18 is an enlarged sectional plan view of the forward part of Fig. 16 taken on the line 18-18 of Fig. 17; Fig. 19 is a sectional elevational View of the forward conveyer on the line 1919 of Fig. 18, to show the relative positions of the forward and rear conveyers; and Fig. 20 on the first sheet of the drawings, is a diagrammatic view of the piping connections for the flow of liquid to operate the plungers of the ceiling jacks of the loading apparatus shown in Figs. 16 and 17, as well as of the loading apparatus shown in Figs. 1, 2, 3, 5 and 6.

Fig. 1 shows the mining and loading machine folded up compact and mounted on a truck 1 which is provided with wheels 2 adapted to travel on the track 3. By means of two rear hydraulic jacks shown at 4,4 in Fig. 6, and one hydraulic jack shown at 5 in Fig. 5, the miningand loading machine may be lifted up off the truck 1 and the lat ter moved out from under the mining and loading machine, after which the mining and loading machine may be moved to the position in the mine where it is to be used. The hydraulic roof jacks 6, 6 at the rear portion of the mining and loading machine, and the hydraulic roof jack 7, shown in Fig. 3 at the forward portion of the machine. may then be relied upon to hold the framework in (its proper position while the cutting and loading operation is being performed.

The mining and loading machine shown in the drawings comprises a circular base plate 8 at the forward portion of the machine, which is provided with a central. hub 9 over which fits the vertical hollow cylinder 10 of the forward hydraulic jack 7 Extending into the upper end of the cylinder 10 is the plunger 11, the lower end of which may be provided with a leather cup packing to form a piston 12, and the upper end of which may be provided with a shoe 13 serrated on its upper surface.

Pivoted to the lower portion of the cylinder 10 is a horizontal plate 14, the forward portion of which is provided with a shoe 15 adapted to slide over the upper surface of the circular base plate 8, as shown in Fig. 3. The forward end of the plate 14 may extend upwardly at 16 to the collar 17 which forms the ivotal connection between the plate 14 and the lower portion of the cylinder 10, as shown in Figs. 3 and 5.

On the lower side of the horizontal plate 14 is a rectangular recess 18 for receiving the pie 19 and the couplings 20 and 21 at its en s. A pipe 22 is also located underneath the plate 14 between the couplings 21 and 23. It will be seen by referring to Figs. 3 and 5 that a passageway 24 is provided through the hub 9 and the base plate 8 to the pipe 19. This establishes communication between the cylinder 10 beneath the piston 12 and the pipe 19. A passageway 25 in the rear portion of the plate 14 con nects the coupling 23 to a pipe 26 which extends to a drum 27 of the electrically operated hydraulic pump mechanism, as shown in Fig. 5. This pump mechanism comprises a pump proper, designated 28 in Fig. 5, an electric motor 29, and intermediate gearing 30. Between the pipe 26 and the drum 27 are two valves, the onedesignated 31 being for the supply and the one designated 32 being for the exhaust. Any suitable type of by 7 drauli pump may be employed in which supply pressure may be obtained by opening the valve 31, and the exhaust controlled by means of the valve '32.

lVhen it is desired to firmly anchor the forward portion of the mining and loading machine in adjusted position, the valve shown in Figs. 6 and 20, will be closed, and the valve 31 opened. Now, when the electric hydraulic pump is operated, hydraulic pressure will be exerted in the pipe 26, and such pressure transmitted to the pipes 22 and 19 and through the passage 24 into the cylinder 10 beneath the piston 12. Continued operation of the hydraulic pump will lift the plunger 11 against the roof of the room in the mine and firmly anchor the shoe 13' in the desired position, and the valve 31 may be closed. The jack 7 will be held in such position until the valve 32 is opened, whereupon the weight of the plunger 11 will cause the water to recede from the cylinder 10 and allow the plunger 11 to descend to a lower position.

At the rear portion of the'mining and loading machine, is located a horizontal connecting plate 33 in an intermediate position,

as shown in Fig. 6, between the rear hydrau- V lic jacks 6 and 6, the latter being in vertical alinement with the floor jacks 4 and 4. The horizontal plate 33 supports the hydraulic pumping mechanism as shown in Fig. 6. The ends of the plate are rigidly connected to the cylinders 34, 34 of the hydraulic acks 6, 6 respectively. Beneath the cylinders 34, 34 are partitions 35, 35 to provide independent cylinders 36, 36 for the hydraulic lifting jacks 4, 4. The roof jacks 6. 6 are provided with plungers 37, 37 which have shoes 38, 38 the latter being preferably serrated on their upper horizontal surfaces. The lifting jacks 4, 4 coinprise plungers 39, 39 which have shoes 40, 40 at their lower ends.

.As shown in Fig. 6, which is a sectional elevational view of Fig. 5, taken on the line 6-6 looking in the direction of the arrows, the lower ends of the cylinders 36, 36 are connected by inwardly extending brackets 41, 41' and the intermediate connecting plate 42. The laterally extending brackets 41, 41' may have forwardly extending portions 43, 43, as shown in Fig. 5, which serve as guides for the longitudinal movement of the conveyer frame 44. At the central portion of the connecting plate 42 is a hydraulic cylinder 45 in which is located a piston 46 at the inner end of the piston rod 47 the latter extending forwardly and being attached to the crosshead 48 at the rear end of'the plate 14.

Pipes 49 and 50 extend between the ends of a set of valves 51, similar to those designated 31 and 32 in Fig. 6, water may be forced into-the cylinder e ahead of the piston 46, or the water may be permitted to be exhausted therefrom. In a similar way, a set of valves 52 may be operated to produce or relieve pressure back of the piston 46. in 5 and 6 l have shown manually op erable jacks comprising screw-threaded rods 53, 53" which are pivoted at 54, 54 to the frame 33 which is attached'to the vertical lifting jack cylinders 36 and 36 respective'ly. 0n the screw-threaded rods 53, 53' are the shoes 55, 55 which may be adjusted to various'angles againstfthe side Walls and moved outwardly by means of the wheels 56, 56. The brackets 217, 217 be provided to limit the rearward adjustment of the manual jacks as indicated by the dotted line positions in Fig. 5, in which positions said jacks may retain the rear portion of the mining and loading machine midway between the mine walls when such rear portion is being moved forwardly in the manner hereinafter described.

"the cylinder 10. so that the plunger may have vertical up and down motion, but is prevented from being rotated. On the plunger 11 is rotated a disc bracket59 which is prevented from turning on the plunger 11 by the featner 60 and which may be fixed in adjusted position by means of the set screw 61. That is to say, the disc bracket 59 cannot turn relatively to the plunger 11 but may be adjusted to variousvertical positions on the plunger 11 and held in adjusted position by means'ofv the set screw'61. At the upper end of the plunger 11 and surrounding the same, is a collar bearing; 62 to which is connected the upper horizontal bracket 63 to the forward end of which 'at 64 is pivoted the cutter-carrying arm 65. The outer end of the arm 65 is provided with a collar hearing 66 in which fits the tubula'r'shaft 67. At

' the upper end of the tubular shaft 67 is located the horizontal disc cutter 68 and beneath the cylindrical collar bearing 66 is a be turned in either direction so as to oscillate the segmental worm gear 73 and thereby tilt the arm 65 and the disc cutter 68 to various angles. It will be seen by referring to F 3, that the bracket 63 is yieldingly counterbalanced by means of the spring 74 on the disc bracket 59 which is fixed to the plunger 11. Surrounding the plunger 11 is a ring 3 5 on ball bearings which rest on the hub portion of the disc 59. The ring 75 is provided with a cylindrical cup 7 6 which telescopes into the cylindrical recess 77 on the under side of the bracket 63 near the cylindrical collar bearing 62. It will therefore be seen that the bracket or arm 63 and the parts carried thereby are in part supported by the spring 74 and the ring 75 on the ball hearings on top of the hub portion of the disc 59. The main support for the bracket 63 is by means of the wheel 7 8 which is pivoted in suitable position in the bracket 63 intermediate its ends, as shown for example in Fig. 3. The wheel 78 rides on the upper cam surface of the disc bracket 59 which cam surface is cylindrical in plan view, as shown in Fig. 7, but which is provided with inclined cam surfaces at 79, 79' so as to vary the elevation of the bracket 63 and cutter 68 at certain periods. This can easily be accomplished because the cylindrical collar 62 is free to slide up and down on the plunger 11, the spring 74 acting as a cushion in the descent'and because of its counterbalancing" action facilitating the ascent.

' At the upper end of the cylinder 10 is mounted a cylindrical collar 80 which may be secured in adjusted position by means of the set screw 81. To the upper end of the cylindrical collar 80 is secured the circular or disc gear 82. At the lower end of the cylindricalcollar 80 is a ring bearing 83 to form a ball race. Between the ring bearing 83 and the under surface of the disc gear 82 and surrounding the cylindrical collar 80, is a freely movable cylindrical collar 84., It will be seen that this collar 84 is connected by ball bearings to the collar 80 and is supported on the ring bearing 82. Securely attached to the freely movable cylindrical collar 84; is a bracket arm 85 which supports a plurality of parts. The bracket arm 85 is an interu'iediate frame for the cutter mechanism, but its principal utility is to support mechanism for rotating this frame 85 as well as the parts connected thereto, including the forward arcuately movable scooping conveyer.

Rigidly connected to the frame 85 and extending upwardly therefrom, is a vertical rod 86 which has a sliding; connection with the arm 63 by fitting into the cylindrical opening 87 which extends vertically through the arm 63, as shown in Fig. 3. By this means whenever the frame 85is moved horineously.

zontally or rotated on an upright axis, the arm 63 will be likewise rotated because of the connection through the rod 86.

Journalled in the upper portion of the frame or arm 85 is a short vertical shaft 88, at the upper end of which a pinion 89 which meshes with the disc gear 82. In the lower portion of the frame 85 is journalled an extension of the shaft 853 at the lower end of which is a gear wheel 9]. which meshes with a pinion 92 which is also mounted in the frame 85, as shown in F 3. Intermediately mounted on the shaft 88 is a gear 98 which meshes with the gear 94:; An electric motor 95, provided with suitable starting mechanism, is mounted in the frame 85 near the cylindrical collar 84. I prefer to mount this motor 95 so that its shaft will occupy a vertical position. Gears 92 and 94 are loosely mounted on the shaft of the electric motor 95-, but the clutch member 96 is splined thereto and may be manually operated by the handle 6, or automatically operated by any suitable means such, for instance, as illustrated in Figs. 10, 11 and 12, so as to connect the motor shaft to either the gear 94 or the gear 92.

It should be understood that the pinion 89, the gears 93 and 91, and the shaft 88 are mounted to rotate together. It will also be observed that the gear 92 is small comared with the gear 91, and that the gear 94 is large as compared with the 93. Therefore, when the gear 92 is thrown in, the pinion 89 will be rotated slowly to effect feeding movement of the cutting mechanism about a vertical axis extending vertically through the center of the forward roof jack. When the gear 94 is thrown in, however, the pinion 89 will be rotated comparatively fast, which should be done when the cutting mechanism is to be moved to a new cutting position after a plurality of kerf cutters have completed a series of cuts simulta- In the event that this mechanism is to be controlled manually, the clutch 96 may be operated each time the speed of rotation is to be changed, by means of the handle 96, this using cone by the operator.

As above stated, I have illustrated in Figs. 10, 11. and 12 a modified construction by means ofwhich the change in speed may be automatically controlled during the rotary movement of the mechanism. Referringto these views it will be seen that a rod 9 6 may be mounted in suitable brackets formed on the collar 84 to reciprocate verticall This rod is constantly urged in a vertical direction in its bearings by means of a spring 96 positioned between a collar on the rod and the lower bearing'of the rod. The lower end of the rod is provided with a forked end in position to engage the handle 96 so that when the rod is reciproeated vertically it will shift the handle 96 to throw the clutch member 96, as previously described. The reci rocation of the rod 96 may be accomplis ed automatically at the proper time by means of a concentric groove 82* formed in the under side of the gear 82, as illustrated in Figs. 10, 11 and 12. This groove or slot 82" extends through an arc of substantially 180 degrees. During the time that the cutting mechanism is in its cutting position, that is during the rotation thereof through the arc in which the cutting of material actually takes place, the rod 96 is held in its lowermost position because its upper end is in contact with the under surface of the gear 82. This position of the arm 96 holds the clutch member 96 in such position as to hold the slow speed gears 91 and 92 in driving relation with the mechanism, as above explained. When the cutting mechanism leaves its cutting position, however, the end 82" of the slot 82 arrives in position to allow the rod 96 to be moved upwardly by the sprin 96 into said slot, and thereby shift the clutch to the high speed set of gears 98 and 94s The cutting mechanism will then travel at a comparatively high speed, as above explained, until it again arrives in cutting position, whereupon the rod 96 will be be forced downwardly out of the slot 82 and thereby shift the clutch back to the slow speed gears. In order that the rod 96 may be properly forced downward out of the groove 82 the end 82 of said groove in clined or formed as a cam, as shown in Fig. 12. The end 82 of the slot or groove 82* may be abrupt since the spring 96 will act to shift the rod 96 upwardly at the proper time. By means of this modified arrange ment, it is unnecessary for the operator to watch the speed changing mechanism since the change in speed will automatically occur at the proper times.

An additional electric motor 97 is also mounted in the frame 85 and preferably in vertical position, as shown in Fig. 3. If desired, the electric motor may be provided with speed changing gears in the casing 98. This electric motor 97 may also be provided with suitable starting and regulating apparatus independently of the electric motor 95, although both motors may be connected to a common source of supply, comprising removable socket switch connections.

At the lower end of the shaft 99 of the electric motor 97, is a pinion 100 whieh meshes with the gear 10l,'the latter being mounted to rotate in the bearing 102 which is supported by means of the bolt 103 and nut 104 at the outer portion of the frame 85,.

as shown in Fig. 3. Thegear .101 meshes with the gear 105'which is located at the lower end of the hub 106 of the disc cutter 107.

Suspended from the frame 85 is an enclosed cylinder 108 in which is located the piston 1.09, the piston rod'110 of which is connected at 111 to the lowermost cutter frame arm 112, as shown in Figs. 1 and 3. Between thev plston 109 and the lower end of the cylinder 108 is a spring 113 which acts on the'piston 109 and constantly tends to lift the arm 112'. The hub portion 114 of the rotatable arm 112 is held between the stops 115 and 116 when the arm 112 is in the position shown in Fig. The stops 115 and 116 are arranged vertically and connected to collars 117 and 118 respectively, which surround the cylinder 10. The stop 115 may be adjusted to various vertical positions along the post 10 and may also be rotated to various positions. After the stop 115 is in the desired position, it will be held there by means of the set screw 119. The stop 116 is similarly adjustable and may be held in adjusted position by means of the set screw 119. The upper surface of the hub 114 may engage the lower end of the stop 115, as shownin 3, and when freed from this stop during rotation, such upper surface may engage the lower surface of the collar 117, as shown in Fig. 1. The hub 114 is cut away at the side opposite the arm 112 so as to form the interlocking member 120 which is shown in Fig. 1. So long as the interlocking member 120 rests on the stop 116, as shown in Fig. 1, the arm 112 is free to be rotated in either direction, but as soon as the arm 112 is rotated to such position that the member 120 is freed from the stop 116, the hub 114 together with the arm 112 is free to descend. It cannot then be moved backwardly but can then be moved forwardly to the point where the member 120 enthe stop 116. The latter therefore assures the proper lifting of the arm 112 together with the hub 114, for if it be attempted to rotate the 112 beyond the point where it should be lifted, such motion will be arrested the stop 116. It should also be observed that the hub 114 is cut away at its upper portion, as indicated at 122 in Figs. 2 and 18, so to be of less diameter over that portion opposite the arm 112. This will permit the hub 114 to move within the stop 115 when in the position shown in Fig.

By referring to Fig. 3, it will be seen that a suflicientspace is provided between the stop 115 and the post 10 for the collar portion of the hub 114 when the arm 112 is in position for upward movement along the post 10. When in the position shown in Fig. 2, the hub 114 is kept from being lifted because the stop 115 is in position to act as an abutment to prevent upward movement of the arm 112 and to hold the latter in the position shown in Fig. 3.

On the lower side of the outer end of the arm 112 is a depending lug 123 which will engage the cam surface 124 when the arm 112 is rotated a sufiicient distance. The cam 124 is arc-shaped in plan View, as shown in Fig. 5, and is securely attached to the upper surface of the rectangular plate 14. The part of the cam 124 which extends from the plate 14 is inclined downwardly so as to be in position to receive the depending lug 123 of the arm 112 and gradually lift the latter. VJ hen the lug 123 engages the cam 124 the hub 114 is in such position that it has run out from under the stop 115 and is free to be lifted. By the time that the end of the camis reached, such cam has lifted the hub 114 to a position where the interlocking member 120 is near the stop 116 and about to ride on top of the same. It will be seen that the lug 123 is of sur'licient length to assure the engagement of the interlocking member 120 with the upper surface of the stop 116 before the lug 123 leaves the cam 124. After the lug 123 leaves the cam 124 the stop 116 will hold the hub 114 and the arm 112 in its uppermost position until the arm 112 and the disc cutter thereon are entirely clear of the conveying apparatus hereinafter described. The stop 116 may be varied in width as desired, b-ut preferably it should be such as'to permit the arm 112 to descend again when the outer end of the same approaches the mine wall and a new cut is about to be made.

lVhen the hub 114 is freed from the stop 115 and the cam 124 lifts the arm 112, the spring 113 shown in Fig; 3 will act as a counterbalance to facilitate such upward motionof the arm 112. The spring 113 also cushions the fall of the arm 112 when the weight of the latter causes the same to de scend after the hub 114 is freed from th stop 116.

At the outer end of the arm 112 is pivoted at 125 the disc-carrying arm 126 which is provided with a cylindrical bearing 127 in which is journalled the tubular shaft 128, as shown in Fig. 3. The lower end of the tubular shaft 128 is provided with a disc cutter 129 mounted in a horizontal position at the base of the mine wall in a plane adj acent the floor of the mine chamber in position to cut a kerf the bottom of which will be approximately in the plane of such floor. At the upper end of the tubular shaft 128 is secured in adjusted position by means of V shafts 137 and 138 respectively to the roll-- ing mill. couplii'igs 139 and 110. The conplings 135, 136, 139 and 1 10 are such as to allow the shafts 137 and 138 to have considerable play sidewise or from a vertical position. Thetubular shafts 67 and 128 have a free sliding vertical motion on the couplings 139 and 1 10 but both must rotate whenever the shafts 137 and 138 rotate. The couplings 135 and 136 are also such that although considerable play may be given to the shafts 137 and 138 rotary motion of the hub 106 will be transmitted to these shafts. In this instance I have shown the couplings 135, 136, 139 and 110 as each comprising four longitudinal fans or feathers on enlargemients at the ends of the shafts 1:37 and 138. On the interior of the tubular shafts 67 and 128 are longitudinal slots in which these fans are slidable. g

By means of the nut 1 11, the worm 1 12 shown in Fig. 1 may be turned to lift or lower the cutter-carrying arm 19.6. The worm 1 12 is journalled vertically in bearings secured to the arm 112 in position to mesh with the segmental worm gear 113 at the inner end of the arm 126. It will therefore be seen that both the uppermost cuttencarrying arm and the lowermost cutter-carrying arm 126 may be moved to various angular positions by means of the worm gearing adjusting mechanism.

' Although I have shown five disc cutters spaced apart and arranged at different elevations, there may be a greater or less number of such cutters. For instance, additional disc cutter could be easily connected to the intermediate frame 85 above or below the disc cutter 107 and secured in adjusted position by means of a set screw 1 similar to the means for fastening the disc cutter 131 or 13 1 in position.

After the forward roof ack has been operated to hold the front portion of the minin and loadin machine firml Y in fixed g position, and it is desired to start the cutting operation, the various disc cutters should have their carrying frames properly adjusted. The lowermost out should be level with the floor of the mine chamber, hence the stop 116 should be low cred and fastened in such adjusted position I by means of the set screw 119. The cylin di'ical collar can be moved up or down along the post 10 within certain limits, to vary the position of the disc cutter 107. The sliding connections at the couplings 139 and 140 will permit free vertical ad- It will also be the cylindrical opening 87 in the frame 63, and the enclosed cylinder 108 can be moved up or down on the piston 1.09. In some cases it is not of importancejust where the cutter 10 7 makes its out and therefore the tension of' the spring 113 in the cylinder 108 may be varied by changing the elevation of the frame 85. By lifting the frame 853 tne spring 113 will be put under greater tension, and by lowering the frame such spring will have less tension. The uncounterbalanced portion of the Weight of the arm 63 would then be carried on the up perinost arc-shaped surface of the cam bracket 59, by means of the roller 78, as shown in Fig. 3.

The cutters 68 and 134 may be arranged in horizontal position or given an angular or inclined position by actuating the nut 70. After all the various parts have been adjusted, the current to the motor 97 may be turned on in the proper direction to rotate the various disc cutters inthe direction indicated by the arrow 14.41 in Fig.

The cutting tools 1 16 will then cut horizontal lcerfs into the mine wall as shown in Fig. 3. The cutting tools 146 may be and preferably are removable or detachable from the cutting discs which carry them so that they may be conveniently'removed and resharpened or a broken tool replaced.

In order to advance the cutters in feed ing direction, the current to the electric motor 95 should be turned on in the proper direction. to rotate the pinion 89 in ananticlockwise direction when viewed in plan. This pinion meshes with the gear 82 which is held in fixed position by the set screw 81 on the post 10. When the clutch 96 is thrown in to effect the rotation of the pinion 92, motion will be transmitted to the gear 91, the shaft 88 and the pinion 89, whereupon the frame 85 will be slowly rotated in the direction indicated by the arrow 1 17 in F 5.. This feeding movement of the frame 85 will be transmitted by means of the vertical rod 86 to the arm 63, the collar 78 of which will guide the arm 63 in a horizontal plane until the incline 79 is reached, when the arm will descend. This descent will not be abrupt, however, because the spring 7 1 will cushion the action, and when theroller 78 again rides upon the cain'surface 79, shown in Figs. 2 and 7, the spring 7 1 will facilitate the ascent, because it acts in the manner of a counterbalance. It should be observed that the cam surfaces 79 and 79' should be so adjusted that when the hori zontal kerfs in the mine wall are completed the arm 63 will be about to descend, and when a new cut is to be made the arm 63 will again ascend to its proper position at the opposite side of the mine wall.

As the frame 85 is rotated, it carries with it the cylinder 108 which acts on the piston 109 and the piston rod 110 to carry along the lowermost frame 112. It will therefore be seen that the coupling shafts 137 and 138 will be maintained in substantially vertical alinement with each other and in vertical alinement with the tubular shafts 67 and 128. The principal .function of the particular type of coupling shown is to permit the uppermost and lowermost cutters to be moved to different angular planes, either 7 horizontal or inclined upwardly or. inclined downwardly.

I prefer to mount on each of the cuttercarrying arms or frames 63, 85 and 112 an electrically operated vertical disc cutter, as shown in Figs. 2, 5 and 8. These vertical disc cutters will each make a cylindrically shaped kerf, as shown at 148 in the diagram of Fig. 15, at the inner ends of the horizontal kerfs 149. A vertical cylindrical kerf made by a vertical disc cutter is also represented in Fig. 14. The arc-shaped dotted line 150 in Fig. 14 represents the path that the vertical disc cutters will take in con tinuing the kerf 148. The shown in Fig. 8, which is a plan sectional view of Fig. 3, taken on the line 8-8, is

' typical of the mechanism for supporting Cit and operating the vertical disc cutters. EX- tending laterally from the frame 85, as shown in Fig.9, is a bracket 152 provided with a vertical opening therethrough into which fits the pin 153 which may be held in vertical adjusted position by means of the set screw 154. At the upper end of the pin 153 is securely attached the horizontal bar 151 at the outer end of which is a fork 156 for supporting the bearings 157 157 for the worm 158, as shown in Fig. 8. A crank 155 affords a means for turning the worm 158 manually. The worm 158 meshes with a worm gear 159 which is mounted for rotation on the bar 151. On the upper surface of the gear 159, at 160, is pivoted the rear end of the electric motor 161.

Extending from the frame of the motor 161 is a comparatively long arm 163, as shown in Fig. 8, the outer end 164 of which forms a means of attaching and holding a bearing 165 for the outer end of the shaft 166. If desired, thebearing 165 may be held in position by means of the bolts 167.

The shaft 166 is preferably coupled to the shaft of the motor 161 by means of the coupling device 168 which will permit the shaft 166 to be removed when desired and replaced by another one. The shaft 166 is preferably made integral with the cutter disc 169. The cutters 170 and 170 may be separate and removable, or integral with the disc. hen the disc cutters 169 need repair, the entire disc, together with the shaft 166, may be easily removed by withdrawing the coupling pin at the coupler 168 and in serting another shaft with a new or sharpened disc cutter thereon. By means of this construction, the disc cutters may be quickly removed, thus saving considerable time. The horizontal disc cutters 184 and 131, shown in Fig. 3, are also readily removable construction and can. be replaced by entire new disc cutters. In a similar manner the other disc cutters may be made removable.

Near the outer end of the arm 163 is pivoted at 171 a trailer 1(2 having a breaking down cam 173 at its outer end and on the under side, as shown in Figs. 2 and 8. There may also be such a cam breaker on the upper side of .the trailer 172, as shown at the upper right hand portion of Fig. 2 at 174. Such a cam breaker on the upper side is particularly useful for breaking down the uppermost slab of coal to be mined. By referring to Figs. 2 and 15, it will be seen that when the horizontal and vertical lrerfs are made, there should be at least one such cam breaker for each slab of coal being cut. For instance, the cam 174 would be relied upon to break down the slab 17 5, the cam 173' to break down the slab 176 and the cam 173 would break down the slab 178.

As shown in 2, the small electric meters 161, 161 and 161 are pivoted at 160, 160 and 160 to the upper surfaces of the worm gears 159. .159 and 159 respec tively. and are yielding-1y held in a sub tantially horizontal position by means of the leaf springs 1'79. 179 and 179. By thus having the small electric motors 161, 16'

effected by the manually operated worm gearing. Each unit also has its motor yieldingly mounted, as shown at 179, 179 and 179. in Fig. 2. Each unit also has a breaker arm pivoted to the arm which extends outwardly from the electric motor, as shown in Fig. 8. Each unit also comprises a bearshaft mg for the outer end of the cutter disc and a coupling at its inner end by which the cutterand its shaft may be easily removed and replaced by a new one. I also prefer to pivot the trailers carrying the breaking down cams. in such a way that they may have a limited oscillating movement whereby they will adjust themselves to the condition of the uts and the material. This lost motionis limited by the shoulders 180, as illustrated in Fig. 8. The electric motors 161, 161 and 161 being carried with the cutterframes 85, 63 and 112 respectively. will remain in substantially vertical aline ment and it will therefore be easy to supply proper wiring for the samefrom the same source of supply that furnishes current to the feeding electric. motor and the cutteroperating motor 97. Since the rotation of the cutter-carrying frame is continuous, the feed wire may be connected to electric slip rings on the ring 17 below the collar 118, where slip rings can be located, insulated from each other but connected to the wires which place the various motors in parallel to each other. (See Fig. 3.) g

* I will now describe the conveyer mechanism and show that it is particularly adapted for use with the kerf cutting mechanism hereinbefore described, in a combined mining and loading machine, although such conveying mechanism may be used without the cutting mechanism described in a simple loading machine. An endless chain 181, as shown in Fig. 5, provided with laterally extending flights 182, extend around a driving sprocket 183. An electric motor 184 is con-- nected directly to the sprocket 183 to drive the latter. The chain 181 travels in the grooves 185, 185 in the lateral faces of the longitudinal plate 14, as shown in Fig. 6. The forward portion of the endless chain 181 extends around the pulley 218 at the lower end of the post comprising the cylinder 10, as shown in Fig. 3. The conveyer trough frame 44 is connected to the longi tudinal plate 14, as shown in Fig. 6 and is provided With vertical flanges 186 and 187, as shown in Fig. 5. However, the vertical flange 187 is broken away adjacent the cams 124 and 216.

As shown in Figs. 2, 16 and 18, the forward portion of the flange 186 is curved to form a trough or receptacle for the flights 182 to travel along and for receiving material from the swinging conveyer 210.

The rear portion of the trough 44 is sup ported directly on the connecting plate 42 and is slidable thereon, as shown in Fig. 3. Mounted upon the plate 42 by being secured thereto, is a ball bearing swivel socket 188 in which is located the swivel or axle 189 of the bracket 190. To the rear end of the bracket 190 are pivoted the vertical arms 192 to the lower end of which is secured the extension 193 of the conveyer trough. It

will be seen by referring to Fig. 1 that this extended conveyer trough is curved upwardly so that mine cars may be run under the same. The lower end of the extension 193 is curved, as indicated at 194 in Fig. 5, so as to make a turntable connection with the rear end of the conveyer trough 44.

To the upper end of the pivoted bracket 190 is pivoted at 195 the screw-threaded rod 196 which extends loosely through the upper end of the lever arm 197 which is secured to the arms 192. By means of the wheel 198 on the screw-threaded portion of the rod 196, the arm 197 can be moved backward to effect the lifting of the extension conveyer trough 193. By turning the wheel 198 backarm 197 and the pivoted support 190. This cushioning device comprises a cylinder 199 pivoted at 200 to the pivoted support 190 and a piston 201 which is connected to the piston rod 202, the latter being pivoted at 203 to the bracket arm 197, as shown in Fig.

3. A spring 204 is located between the piston 201 and the end of the cylinder 199 opposite the pivotal point 200. The spring 204 counterbalances nearly all of the weight of the conveyer trough extension 193, so that by turning the wheel 198 the extension may easily be lifted. The counterbalanced weight of the extension should be sufliciient, however, to lower the same against the action of the spring 204 when the wheel 198 is turned in a direction to release the arm 197.

I have not shown power opcrated or automatic mechanism for swinging the extension 193 about its pivot 189 as this can easily be done manually. The connection between the rear end of the conveyer trough 44 and the extension 193 is maintained by the adjacent arcu ate ends indicated at 194. The parts at 194 are determined by the pivot 189 as a center. The conveyer chain 181 may be suificiently slack and flexible to permit the desired lateral movement of the conveyer trough extension 193.

At the forward portion of the mining machine is a supplemental conveyer, as shown in Figs 5, 18 and 19, comprising an endless chain 205 which is arranged to be operated by an electric motor 206 geared to the chain 205 having laterally extending flights 207 which move in the conveyer trough 208 at the forward end of which is the vertical flange 209 joining the vertical flange 210. The forward portion 211 of the. conveyer trough is hinged at 212, 212 so as to allow such forward portion to occupy a substantiallyhorizontal position, although the main portion may occupy various inclinations,

such for instance as that shown in Fig. 19.

The conveyer trough 208 and parts mounted thereon, including the electric motor 206, are supported by means of the bracket arm 213 which extends laterally from the cutterframe 112, as shown in Fig. 5. is pivotally connected at 214 to the supplemental conveyer. This pivotal connection 214 will permit vertical movement of the lowermost cutterframe 112 and also of the rear portion of the supplemental conveyer, while the forward portion of the latter remains on the floor of the mine chamber. The forward lateral edge 215 of the supplemental conveyer trough, will then exercise its maxium efiiciency in acting as a scoop for The arm 213 cOllGCting substantially all material in its path. As aboveindicated, the supplemental conveyer must be lifted or elevated to such position that it will pass over the main conveyer during the portion of the rotation of the cutting apparatus when in non-cutting 7 position, and for. this reason 1' provide an arc-shaped cam 216 similar to the arcshaped cam 124, the cam- 216 being located farther in the rear or behind the cam 124, as shown in Figs. 2, 3 and 5. When the lug 123, shown on the lower side of the cutter frame 112 in Fig. 3, engages the cam 124:, the arm 213 will be lifted, and therefore the rear portion of the supplemental conveyer will be lifted. lVhen the lug 123 with respect to its center of rotation, is about on the section line 11-11 of Fig. 10,. the rear portion of the supplemental conveyer will be in the position represented in Fig. 19. During the lifting of the rear portion of'the supplemental conveyer, the outer or scooping end is dragged-toward the base plate 8 and therefore will be brought nearer the center of rotation, that is, the vertical axis of the cylinder 10. At such time, however, the frame 112 is substantially at its uppermost limit of travel and the outer or scooping end of the conveyer will be in position to engage and ride up on the cam 216 asthe cutter frame 112 continues to rotate. The free end of the supplemental conveyer will thus be lifted up over the main conveyer. The parts are properly proportioned to assure the holding of the supplemental con veyer clear of the main conveyer. When the lug 123 becomes disengaged from the cam 124, the stop 116 still holds the cutterframe 112 in its elevated position. After the outer end of the supplemental conveyer leaves the cam 216, it may safely drop clear of the main conveyer. Then when the cutting operation is about to be repeated, the stop 116 will be engaged and the frame 112 will descend to its lowermost position, as shown'in Fig. 3, whereupon the rear end of the supplemental conveyer will againfdescend and engage the upper end of the flange 186 or outer wall of the conveyer trought l. As the cutters areadvanced to .produce the horizontal and vertical cuts the breakers 011 the trailers continue to break down the coal which is scooped up and moved by means of the conveyer flights 207 onto the main conveyer, where the con veyer flights 182 will move the coal to the extension 193 and thence out into mine cars on a mine track lead along the mine chamber to a position under the overhanging conveyer extension 193. V

By referring to'Figs. 16, 18 and 19 it will be seen that the gathering conveyer is connected at 214.- to the frame 112 so as to have at 2145 and also to have a bodily swinging this run-way.

discharge conveyer comprise non-traveling belt run-ways.

Each conveyer also comprises an endless transmission belt carrylng spaced lights which traverse the run-ways.

The line of draft of the delivering or discharge conveyer extends forwardly and around the vertical axis so that the receiver comprising the vertical wall 186 will be open to this line of draft. The line of draft of the gathering conveyer may be on either side of the endless belt because the motor 206 is an electric motor and may be reversed so that the flights 207 may traverse the ways alternately at the forward and return portions of the belt. This is advantageous to loosen the material particularly along the run-way in advance of the upright wall 210 when material tends to become choked along In other words, the reversibility of the transmission belt 205 relieves choking conditions which may occur under some circumstances.

By referring to Fig. 19 it will be seen that the reversible traveling conveyer flights which traverse the ways on the pan 208 sweep in horizontal arcs at oppositeends of the ways and at the discharge end the flights have a free sweep from one way to the other, the receiver being disposed beneath the discharge end of the gathering conveyer. It will also been seen that the ways which lead out of the receiver provide the base of the latter. Furthermore the reversibility of the belt 205 renders the ways on the pan 208 alternately available for conveying the material in a common draft direction from the floor to the opening above the receiver. \Vhen the flights 207 move across the upper end of one way to the upper end of the other they have a non-conveying armv arc sweep. In other words, duplex ways are provided on the pan 208 and the reversible transmission belt 205 carries spaced flights which may traverse the ways alternately in the forward and return portions of the belt and in a horizontal non-conveying are from one way to the second. When the scooping attachment comprising the plate 211 and the vertical wall 209 is hinged to the pan. 208, as

shown at 212and 212, the gathering conveyer is intended to operate only in one direction of horizontal sweep over the mine floor in advance of-the supporting framework, but when the scooping attachment is omitted by removing the hinges 212, 212',

the gathering conveyer may be swept arcuately across the mme floor in opposite direc- 112 and" the framework on which it is mounted. It should also be noted that the upright axis of swinging movement of the gathering conveyer and the supplemental frame 112 coincides with the axis of relative swinging movement of the forward frame 8 and the rear frame on which the delivering conveyor is mounted. This upright axis of swinging movement of the gathering conveyer also coincides with the forward upright axis of the areuate bearing for the chain 181, the latter being driven by the motor 184; and the rear-"section 193 being swingable horizontally for the purpose of delivering material to mine cars on a track directly back of the longitudinal length of the machine or to mine cars on tracks on opposite sides of the longitudinal length of the machine.

It should be understood that although the stop 116 by engaging the interlocking mem her 120 of the arm 112, holds the latter in its uppermost. position even after the lug runs off the cam 124: shown in Fig. 5, the arm 112 should drop to its lowermost position just as soon as the conveyer trough 44 is entirely cleared. This operation is desired so that the disk cutter 129 will be ready for operation just as soon as it approaches the wall of the mine. -The supple mental conveyer trough 208 will also descend .at its outer end while the lug 123. on the under side of the conveyer trough 208 is still on the cam 124. It-should be understood that the parts may be so related that the lug 123 on the bottom of the trough 208 will be approximately at the same distance from the vertical central axis of the post 10 as the lug 123 on the arm 112 and as the cam 121. The cam 216 serves as an additional support for the conveyer trough, or may be used as the sole support of the conveyer trough when the latter is lifted too high for the lug 123 to engage the cam 124. However. the lug 123' will not run off the cam 124 radially because the lug and cam are of sufficient width to prevent this. The lug 123 will finally run off the cam 124 a short time after the conveyer trough 208 runs off the cam 216. The conveyer will then drop onto the flange or sidewall 186 of the main conveyer.

trough 44, and continued rotation of the supplemental'conveyer trough 208 will allow the latter to return to its lowermost po 19. As soon as the a'rm'112 and the parts carried thereby are entirely clear of the conveyer trough 44, the arm 112 will drop and the rear end of the supplemental conveyerwill also descend. The forward end of the sup elemental conveyer, however, will still be e evated by the cams 124 and 216. Continued rotation of the supplemental conveyer will finally cause the forward portion thereof to reach its scooping position on the floor of the mine chamber. As the horizontal disc cutters produce the horizontal kerfs, and the vertical rotary cutters produce the vertical kerfs, the trailers carrying the breaking down cams are continually effecting the breaking off of the coal in large pieces which fall onto the supplemental conveyer trough 208 or onto the floor" at the base of the mine wall in position to be scooped up by the scooping edge 215 onto the platform 211 from which the coal is conveyed by the flights 207 to the main hopper at the forward end of the conveyer trough while the flights 182 move the pieces of coal to the extension 193 and thence into the minecars. It should be particularly observed that by employing intermediate vertical disc cutters following the horizontal disc cutters, the coal may be broken down in large pieces. This is because a disc cutter can produce deeper cuts than tools which move in arcs of circles but do not rotate. In the construction shown in the drawings, a single rotary disc cutter produces a vertical kerf which extends both above and below the horizontal kerf and communicates with the latter, as shown in Fig. 15. By referring to the latter view, it will be seen that the uppermost slab 175 and the lowermost slab 17 8 are not as thick as the intermediate slabs 17 6 and 177. The intermediate slabs can be made larger because of the rotary disc cutters wlhich extend into the coal above and below the horizontal kerfs. Furthermore, the additional weight of the larger intermediate slabs will assist in breaking them loose from the mine wall. By this method of mining coal vertical arc-shaped kerfs are produced by rotary disc cutters at one operation. such vertical kerfs communicating with the horizontal kerfs to out large intermediate slabs which are broken down by means of the cams at the ends of the trailers loosely connected to the vertical disc cutter-carrying arms. Therefore the horizontal kerfs are each completed by a single rotary disc cutter, and each of the arc-shaped vertical kerfs is produced by a single vertical disc cutter. Only a single cam or wedge acts for breaking down acertain slab of coal which has been cut, as indicated in Fig. 15. The mining operation is 

